CN104006152A - Method for predicting reactive clutch loads and preemptively adjusting line pressure - Google Patents

Method for predicting reactive clutch loads and preemptively adjusting line pressure Download PDF

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Publication number
CN104006152A
CN104006152A CN201410059025.9A CN201410059025A CN104006152A CN 104006152 A CN104006152 A CN 104006152A CN 201410059025 A CN201410059025 A CN 201410059025A CN 104006152 A CN104006152 A CN 104006152A
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CN
China
Prior art keywords
power assembly
torque
prediction
clutch
engine
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Granted
Application number
CN201410059025.9A
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Chinese (zh)
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CN104006152B (en
Inventor
K.P.帕特尔
S.W.麦格罗根
L.A.卡明斯基
P.古普塔
A.K.纳维
A.H.希普
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GM Global Technology Operations LLC
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GM Global Technology Operations LLC
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/102—Actuator
    • F16D2500/1026—Hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/104—Clutch
    • F16D2500/10406—Clutch position
    • F16D2500/10412—Transmission line of a vehicle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/30—Signal inputs
    • F16D2500/306—Signal inputs from the engine
    • F16D2500/3065—Torque of the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/30—Signal inputs
    • F16D2500/306—Signal inputs from the engine
    • F16D2500/3065—Torque of the engine
    • F16D2500/3066—Torque change rate of the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/70—Details about the implementation of the control system
    • F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
    • F16D2500/70402—Actuator parameters
    • F16D2500/70406—Pressure

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Control Of Transmission Device (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

A method for adjusting hydraulic line pressure applied to one or more clutch devices in an electro-mechanical transmission mechanically-operatively coupled to an internal combustion engine and at least one electric machine includes predicting a first plurality of powertrain parameters for an upcoming event. For each of a plurality of engine torques, a predicted output torque and a predicted clutch load are determined that minimize a total powertrain operating cost based on an operator torque request and the predicted first plurality of powertrain parameters. Hydraulic line pressure is adjusted based on the engine torque having a lowest powertrain operating cost among the plurality of available engine torques.

Description

For predicting reaction clutch load and the method for the adjutage linear pressure of trying to be the first
Technical field
The disclosure relates to the control system for electric mechanical speed changer, and relates more specifically to the control of oil hydraulic circuit.
Background technique
Statement in this part only provides the background information relevant to the disclosure.Therefore, this statement is not intended to form admission of prior art.
Known power assembly structure comprises moment of torsion generating apparatus, and it comprises explosive motor and motor, its by gear arrangement to output link transfer of torque.Output link may be operably coupled to for the power train of automotive to come to its transmission tractive torque.The motor operating as motor or generator be independent of from the input torque of explosive motor generate the input torque of going to speed changer.Motor can convert the vehicle energy transmitting by traffic tool power train to can be stored in electrical energy storage device electric energy.Control system monitoring is from the traffic tool and operator's various inputs, and provide the operation of power assembly is controlled, comprise and control transmission operating range state and gear gearshift, control torque generating apparatus, and the electric power of adjusting between electrical energy storage device and motor exchanges, in order to manage the output of speed changer, comprise moment of torsion and rotational speed.
Speed changer allows the transition between a plurality of operating range states.Transition from from an operating range state to another operating range state can relate at least one clutch state of transition.Clutch state can comprise: the ON state that indication clutch is activated and engages; With the OFF state of indicating clutch to be deactivated and to be disengaged.Transition between clutch state comprises in order to reduce or to eliminate the control measure of the transition period generation clutch slip between clutch state.When reaction load is transmitted through clutch, clutch engages with minimum clutch moment of torque energy force retaining, to avoid slippage.Clutch moment of torque ability is the function that is applied to the hydraulic pressure of clutch.Therefore, the hydraulic pressure in clutch is larger, and the fastening force in clutch is larger, and the clutch moment of torque ability of gained is higher.Therefore, hydraulic control system adopt the pipeline be filled with hydraulic oil optionally to start and joined speed variator in clutch.
Be known that only the estimating clutch load based on current is may cause the reaction mode that the non-required response time increases to come control valve linear pressure to realize the required torque ability in clutch.In general, the increase that is applied to the load of clutch is limited to clutch capacity and in response to a small amount of of estimating clutch load, repeats to change the speed that occurs to increase and how soon have, and it is finally driven by the variation of operator's torque request.The response time of this increase is non-required, because be applied to the variation that the reaction load of clutch must be waited for operator's torque request.In addition, torque capability is necessary to be increased in some cases, although operator's torque request does not change.This may cause hydraulic line pressure not enough, thereby causes the steerability of cltuch slipping and reduction.
It is further known and implement general about logic, it generates " surplus (headroom) " by the line pressure that is applied to clutch being increased to a predetermined nargin for being applied to the possible increase on the horizon of the reaction load of clutch.Yet, clutch load is increased once predetermined nargin and need to have alone nargin even as big as allowing fully response and be minimized to make trading off between the nargin of hydraulic pumping minimization of loss.Therefore the predetermined nargin that, maintains the line pressure that is applied to clutch may cause response time of increasing and the fuel economy of reduction.
Summary of the invention
A kind of for regulating the method for hydraulic line pressure, described hydraulic line pressure is applied to the one or more clutch device in electric mechanical speed changer, described electric mechanical speed changer by mechanically actuated be attached to explosive motor and at least one motor, described method is included as first group of a plurality of power assembly parameter of event prediction on the horizon.For each in a plurality of Engine torques, based on operator's torque request and first group of a plurality of power assembly parameter predicting, to determine prediction output torque and predict clutch load, it minimizes total output assembly running cost.Based on described a plurality of Engine torques in Engine torque with minimum power assembly running cost that obtain, regulate hydraulic line pressure.
The present invention also provides following technological scheme:
1. for regulating the method for hydraulic line pressure, described hydraulic line pressure is applied to the clutch device in electric mechanical speed changer, described electric mechanical speed changer by mechanically actuated be attached to explosive motor and at least one motor, described method comprises:
Based on operator's torque request, be first group of a plurality of power assembly parameter of event prediction on the horizon;
Based on first group that predicts a plurality of power assembly parameters, for a plurality of each that obtain in Engine torque, determine and make the minimized prediction clutch of total output assembly running cost load and prediction output torque; And
From described, a plurality ofly obtain the Engine torque based on thering is minimum power assembly running cost Engine torque and regulate hydraulic line pressure.
2. the method as described in technological scheme 1, wherein, when when having the definite prediction clutch load of Engine torque of minimum power assembly running cost and be greater than estimating clutch load, regulates hydraulic line pressure.
3. the method as described in technological scheme 2, wherein, is adjusted to hydraulic line pressure to maintain the minimum hydraulic pressure line pressure that has the definite prediction clutch load of the Engine torque of minimum power assembly running cost for being embodied as.
4. the method as described in technological scheme 1, wherein, determines the Engine torque with minimum power assembly running cost by gold ratio function of search.
5. the method as described in technological scheme 4, wherein, gold ratio function of search carrys out to determine the Engine torque with minimum power assembly running cost in the following manner:
Monitor each obtainable Engine torque and make minimized each the corresponding prediction output torque of total output assembly running cost;
Monitor second group of a plurality of power assembly parameter;
Based on described second group of a plurality of power assembly parameter, for each obtainable Engine torque and each, predict accordingly output torque and determine power assembly running cost; And
Based on determined power assembly running cost, from a plurality of obtainable Engine torques, select to have the Engine torque of minimum power assembly running cost.
6. the method as described in technological scheme 1, wherein, comprises for first group of a plurality of power assembly parameter of the prediction of event on the horizon: for the prediction clutch state of described clutch device; Prediction output torque; Prediction engine speed; The prediction motor torque limit; The prediction clutch moment of torque limit; With the prediction electrical energy storage device power limit.
7. the method as described in technological scheme 5, wherein, described second group of a plurality of power assembly parameter comprise: electrical energy storage device charged state; Output speed; With operator's torque request.
8. the method as described in technological scheme 1, wherein, described event on the horizon comprises shift of transmission, the combination in any that output torque changes and Engine torque changes.
9. the method as described in technological scheme 1, wherein, power assembly running cost is the factor based on relevant with electrical energy storage device utilization ratio with traffic tool steerability, fuel economy, discharge.
10. for regulating the method for hydraulic line pressure, described hydraulic line pressure is applied to the one or more clutch device in electric mechanical speed changer, described electric mechanical speed changer by mechanically actuated be attached to explosive motor and at least one motor, described method comprises:
Based on operator's torque request, be first group of a plurality of power assembly parameter of event prediction on the horizon, described event on the horizon comprises shift of transmission, the combination in any that output torque changes and Engine torque changes;
For have separately in corresponding a plurality of a plurality of engine conditions that obtain Engine torque each,
Based on first group that predicts a plurality of power assembly parameters be described a plurality of each acquisition in Engine torque be identified in one or more clutch device each prediction clutch load and make the minimized prediction output torque of total output assembly running cost, and
From described a plurality of Engine torques of selecting to have minimum power assembly running cost Engine torque that obtain; And
Final Engine torque based on having minimum power assembly running cost from a plurality of engine conditions regulates hydraulic line pressure.
11. methods as described in technological scheme 10, wherein, from described a plurality of acquisition, Engine torque, select the Engine torque with minimum power assembly running cost to comprise:
For the first engine condition of a plurality of engine conditions is from obtaining the Engine torque that Engine torque selects to have minimum power assembly running cost for the first engine condition a plurality of;
For the second engine condition of a plurality of engine conditions is from obtaining the Engine torque that Engine torque selects to have minimum power assembly running cost for the second engine condition a plurality of;
For the trimotor state of a plurality of engine conditions is from obtaining the Engine torque that Engine torque selects to have minimum power assembly running cost for trimotor state a plurality of; And
For the 4th engine condition of a plurality of engine conditions is from obtaining the Engine torque that Engine torque selects to have minimum power assembly running cost for the 4th engine condition a plurality of.
12. methods as described in technological scheme 11, wherein,
Described the first engine condition comprises that all cylinders are all supplied to fuel;
Described the second engine condition comprises that all cylinders are not supplied to fuel;
Described trimotor state comprises that half cylinder is supplied to fuel; And
Described the 4th engine condition comprises that half cylinder is not supplied to fuel.
13. methods as described in technological scheme 10, further comprise:
Before regulating hydraulic line pressure, from a plurality of engine conditions, to the final Engine torque application with minimum power assembly running cost, stablize cost, the amplitude that described stable cost has is enough to avoid the engine condition from corresponding to described final Engine torque to be vibrated.
14. the method as described in technological scheme 10, wherein, when being greater than estimating clutch load for the definite prediction clutch load of described final Engine torque, regulates hydraulic line pressure.
15. the method as described in technological scheme 14, wherein, is adjusted to hydraulic line pressure to maintain for being embodied as the minimum hydraulic pressure line pressure of the definite prediction clutch load of described final Engine torque.
16. methods as described in technological scheme 10, wherein, from each a plurality of Engine torques for a plurality of engine conditions, select to have in the following manner the Engine torque of minimum power assembly running cost:
Monitor each obtainable Engine torque and make minimized each the corresponding prediction output torque of total output assembly running cost;
Monitor second group of a plurality of power assembly parameter;
Based on described second group of a plurality of power assembly parameter, for each obtainable Engine torque and each, predict accordingly output torque and determine power assembly running cost; And
Based on determined power assembly running cost, from each a plurality of obtainable Engine torque for a plurality of engine conditions, select to have the Engine torque of minimum power assembly running cost.
17. methods as described in technological scheme 16, wherein, described second group of a plurality of power assembly parameter comprise: electrical energy storage device charged state; Output speed; With operator's torque request.
18. methods as described in technological scheme 16, wherein, described minimum power assembly running cost is associated with traffic tool steerability, fuel economy, electrical energy storage device utilization ratio and discharges relevant running cost.
19. methods as described in technological scheme 10, wherein, comprise for first group of a plurality of power assembly parameter of the prediction of event on the horizon: for the prediction clutch state of one or more clutches; Prediction output torque; Prediction engine speed; The prediction motor torque limit; The prediction clutch moment of torque limit; With the prediction electrical energy storage device power limit.
20. 1 kinds for controlling the equipment of power assembly, comprising:
Electric mechanical speed changer, its by mechanically actuated be attached to explosive motor and at least one motor, described explosive motor and at least one motor are suitable for being come to output link transmit machine power optionally by the clutch device of hydraulically start via selectivity start is one or more; With
Controller, it is embodied in control module, comprises
Predictability power assembly parameter module, it is configured in order to predict first group of a plurality of power assembly parameter in event on the horizon;
Optimize module, it is configured in order to based on operator's torque request and the first group of a plurality of power assembly parameter predicting, and is a plurality of each the definite minimized prediction clutch of total output assembly running cost load and prediction output torques of making that obtain in Engine torque; With
Line pressure control module, it is configured in order to regulate based on described a plurality of Engine torques in Engine torque with minimum power assembly running cost that obtain the hydraulic line pressure that is applied to clutch device.
Accompanying drawing explanation
Referring now to accompanying drawing, by way of example, one or more embodiments are described, in accompanying drawing:
Fig. 1 shows according to an exemplary hybrid power assembly of the present disclosure, and it comprises the hybrid gearbox that is operatively connected to motor and the first and second motors;
Fig. 2 shows according to the representative configuration for control system and power assembly of the present disclosure;
Fig. 3 is the schematic diagram according to oil hydraulic circuit of the present disclosure;
Fig. 4 shows according to a kind of controller of the present disclosure, one or more clutch load that started clutch device of its hybrid power assembly for prognostic chart 1, and adjusting is applied to one or more hydraulic line pressure that started clutch device; And
Fig. 5 shows the flow chart that regulates the hydraulic line pressure that is applied to one or more clutch device according to the optimal controller with Fig. 4 of the present disclosure.
Embodiment
With reference now to accompanying drawing,, content shown in it is just in order to illustrate the object of some exemplary embodiment rather than in order to limit their object, Fig. 1 and 2 has drawn an exemplary electronic mechanical mixing power assembly.This exemplary electronic mechanical mixing power assembly comprises double mode, compound distribution, electric mechanical hybrid gearbox 10, and it is operatively connected to motor 14 and the first and second motors (MG-A) 56 and (MG-B) 72.Motor 14 and the first and second motors 56 and 72 each self-generatings can be transferred to the power of speed changer 10.The power that is generated and be transferred to speed changer 10 by motor 14 and the first and second motors 56 and 72 is described by following term: input torque, it is hereinafter referred to as T in this article i, T aand T b; And speed, it is hereinafter referred to as N in this article i, N aand N b.
Exemplary engine 14 comprises multi cylinder explosive motor, and they are optionally operation in several states, in order to moment of torsion is transferred to speed changer 10 via input shaft 12, and can be spark ignition or compression ignition engine.Motor 14 comprises the bent axle of the input shaft 12 that is operatively attached to speed changer 10.The rotational speed of rotation speed sensor 11 monitoring input shafts 12.Power output from motor 14, comprises rotational speed and output torque, can be different from the input speed N that reaches speed changer 10 iwith input torque T i, reason is owing to placing torque consumption parts on the input shaft 12 between motor 14 and speed changer 10, for example, and oil hydraulic pump and/or torque management device.
Exemplary speed changer 10 comprises three planetary gear set 24,26 and 28 and four torque transmissions that optionally engage, i.e. clutch C1 70, C2 62, C3 73 and C4 75.As used herein, clutch refers to the friction torque transmitting set of any type, for example, comprise single-deck or compound disk clutch or sheet, band clutch and break.Hydraulic control circuit 42, it is preferably controlled by transmission control module (TCM) 17, operates in order to solenoidoperated cluthes state.Clutch C2 62 and C4 75 preferably include the spin friction clutch of hydraulic actuation (applied).Clutch C1 70 and C3 73 preferably include the fixing device of hydraulic control, and it can be connected to gearbox 68 by shelves optionally.Each in clutch C1 70, C2 62, C3 73 and C4 75, preferably by hydraulically start, optionally receives pressurized hydraulic oil via hydraulic control circuit 42.
The first and second motors 56 and 72 preferably include three-phase AC machine, and it comprises stator and rotor separately, and corresponding solver 80 and 82.Motor stator for each machine is connected to the outside of gearbox 68 by shelves, and comprises stator core body, and described stator core body has from the electric winding of the coiling of its extension.Rotor for the first motor 56 is supported in hub plate gear, and described hub plate gear is operatively attached to axle 60 via the second planetary gear set 26.Rotor for the second motor 72 is attached to cover propeller boss 66 regularly.
Each in solver 80 and 82 preferably includes variable reluctance device, and it comprises resolver stator and solver rotor.Solver 80 and 82 is properly positioned, and is assembled on corresponding in the first and second motors 56 and 72.The stator of corresponding one in solver 80 and 82 is operatively connected to one of stator for the first and second motors 56 and 72.Solver rotor is operatively connected to the rotor for corresponding the first and second motors 56 and 72.Each in solver 80 and 82 is by signal ground and be operatively connected to speed changer power inverter control module (TPIM) 19, and each self-sensing and monitoring solver rotor are with respect to the rotational position of resolver stator, thereby the rotational position of corresponding in monitoring the first and second motors 56 and 72.In addition, from the signal of solver 80 and 82 outputs, explained the rotational speed that is provided for respectively the first and second motors 56 and 72, be N aand N b.
Speed changer 10 comprises output link 64, axle for example, and the power train 90 that it is operably connected to for the traffic tool, provides outputting power, and for example, to traffic tool wheel 93, one of them is shown in Figure 1.Outputting power is characterized as being output rotational speed N owith output torque T o.Rotational speed and the sense of rotation of speed changer output speed sensor 84 monitoring output links 64.Each in traffic tool wheel 93 is preferably equipped with and is suitable for monitoring wheel speed V sS-WHLsensor 94, its output is monitored by the control module of the distributed control module system of describing with respect to Fig. 2, in order to determine vehicle speed and for braking the absolute and relative wheel speed of control, traction control and traffic tool acceleration management.
Input torque from motor 14 and the first and second motors 56 and 72 (is respectively T i, T aand T b) as from fuel or be stored in the electromotive force in electrical energy storage device (ESD) 74 transformation of energy result and generate.ESD 74 is attached to TPIM 19 via direct current transmission conductor 27 by high-voltage direct-current.Transmission conductor 27 comprises contactless contactor 38.When contactless contactor 38 is closed, under normal operation, electric current can flow between ESD 74 and TPIM 19.When contactless contactor 38 is disconnected, the current flowing between ESD 74 and TPIM 19 is interrupted.TPIM 19 transmits electric power to and from the first motor 56 by transmission conductor 29, and TPIM 19 transmits electric power to and from the second motor 72, in response to realizing input torque T for the torque command of the first and second motors 56 and 72 by transmission conductor 31 similarly aand T b.According to ESD 74, be recharged or discharge, electric current is transmitted to and from ESD 74.
TPIM 19 comprises a pair of power inverter and corresponding motor control module, and it is configured to receive torque command control inverter state thus, thereby provides motoring or regeneration function to meet the motor torque T ordering aand T b.Power inverter comprises known complementary three-phase drive electronic device, and comprise separately a plurality of igbts, for converting the DC dynamo from ESD 74 to ac power, for switching as corresponding one of the first and second motors 56 and 72 power is provided by take high frequency.Igbt forms the switching mode power source that is configured to receive control command.For each each phase place in three phase electric machine, conventionally there is a pair of igbt.The state of igbt is controlled to provide motoring machinery power to generate or electric power regeneration function.Three-phase inverter receives or supplies with direct electromotive force via direct current transmission conductor 27, and it is transformed into three phase current power or becomes it from three phase current power-supply change-over, described three phase current power is gone to by conduction via transmission conductor 29 and 31 respectively or from the first and second motors 56 and 72 that operate as motor or generator.
Fig. 2 is the schematic block diagram of distributed control module system.Element described below comprises the subgroup of whole traffic tool control structure, and provides the coherent system of the exemplary power assembly to describing in Fig. 1 to control.The information that distributed control module system synthesis is relevant and input; and thereby executive routine is controlled various actuators realization control objects; comprise the object that relates to fuel economy, discharge, performance, steerability and hardware protection, described hardware comprises battery and the first and second motors 56 and 72 of ESD 74.Distributed control module system comprises engine control module (ECM) 23, TCM 17, battery pack control module (BPCM) 21 and TPIM 19.Mixing control module (HCP) 5 provides the monitoring control of ECM 23, TCM 17, BPCM 21 and TPIM 19 and coordinates.User interface (UI) 13 is operatively connected to a plurality of devices, is controlled or guided the operation of electric mechanical hybrid power assembly by their vehicle operator.These devices comprise: by it, determine the control of cruising of accelerator pedal 113 (AP), operator's brake petal 112 (BP), Transmission gear selector 114 (PRNDL) and the vehicle speed of operator's torque request.Transmission gear selector 114 can have the operator selectable of discrete number and select position, comprises allowing the sense of rotation of the output link 64 of one of forward and reverse direction.
Aforementioned control module is communicated by letter with other control module, sensor and actuator via local area network (LAN) bus 6.The structured communication of the actuator command signal between the various control modules of LAN bus 6 permission and the state of operating parameter.The concrete communication protocol adopting is specific to application.LAN bus 6 and suitable agreement provide aforementioned control module and provide such as the firm information between other control module of the functions such as ABS (Anti-lock Braking System), traction control and intact stability transmits and the handing-over of multi-control module.A plurality of communication buss can be used for improving communication speed and signal redundancy and the integrity of certain level are provided.Also can use for example serial peripheral interface (SPI) bus of direct link, realize the communication between individual control module.
HCP 5 provides the monitoring of power assembly is controlled, for coordinating the operation of ECM 23, TCM 17, TPIM 19 and BPCM 21.Based on from user interface 13 with comprise the various input signals of the power assembly of ESD 74, HCP 5 generates various instructions, comprising: operator's torque request (T o_REQ); Order output torque (T to power train 90 cMD); The instruction of motor input torque; Be used for torque transfer clutch C1 70, the C2 62 of speed changer 10, the clutch moment of torque of C3 73, C4 75; With the torque command that is respectively used to the first and second motors 56 and 72.
ECM 23 is operatively connected to motor 14, and brings into play function and obtain the data from sensor, and by a plurality of discrete lines, carrys out the actuator of control engine 14, and described discrete lines for the sake of simplicity property is shown as the bidirectional interface cable 35 of merging.The motor input torque instruction that ECM 23 receives from HCP 5.ECM 23 determines actual motor input torque T i, its engine speed and load based on monitoring is provided to speed changer 10 at this time point place, and it is communicated to HCP 5.ECM 23 monitorings, from the input of rotation speed sensor 11, are determined the motor input speed to input shaft 12, and it changes into speed changer input speed N i.ECM 23 monitorings, from the input of sensor, are determined to comprise for example state of other engine operation parameters of mainfold presure, engineer coolant temperature, ambient air temperature and external pressure.Can, for example from mainfold presure or the alternatively operator's input to accelerator pedal 113 from monitoring, determine engine load.ECM 23 generates and communication instruction signal carrys out control engine actuator, comprises for example fuel injector, ignition module and throttle control module.
TCM 17 is operatively connected to speed changer 10, and monitoring is from the input of sensor, determines the state of transmission operating parameter.TCM 17 generates and communication instruction signal is controlled speed changer 10, comprises and controls hydraulic control circuit 42.Input from from TCM 17 to HCP 5 comprises: for each clutch, be the estimating clutch moment of torsion of C1 70, C2 62, C3 73 and C4 75; Rotation output speed N with output link 64 o.Other actuator and sensor can be used for providing the additional information from TCM 17 to HCP 5, reach control object.TCM 17 monitorings are from the input of pressure switch, and optionally activate gearshift solenoid valve and the electromagnetic pressure control valve of hydraulic control circuit 42, optionally activate each clutch C1 70, C2 62, C3 73 and C4 75, thereby realize various transmission operating range states, as the following describes.
BPCM 21 is connected to sensor by signal ground and monitors ESD 74, comprises the state of electric current and voltage parameter, and the information of the parameter state of the battery of indicating ESD 74 is provided to HCP 5.The parameter state of battery preferably includes battery charging state, cell voltage, battery temperature and obtainable battery electric quantity, is called as P bAT_MINto P bAT_MAXscope.
Control module, module, control gear, controller, control unit, processor and similar terms mean with lower any or one or more various combinations: specific integrated circuit (ASIC), electronic circuit, carry out the central processing unit (CPU) (being preferably microprocessor) of one or more software or firmware program or routine and the internal memory being associated and storage (read-only, able to programme read-only, random access, hard disk drive etc.), combinational logic circuit, input/output circuitry and device, suitable Signal Regulation and buffer circuit, and in order to provide other parts of representation function.Software, firmware, program, instruction, routine, code, algorithm and similar terms mean to comprise any instruction group of calibration and question blank.Control module has the one group of control routine that is performed to provide required function.Routine is such as being performed by central processing unit (CPU), and is exercisable, the input in order to monitoring from sensing device and other network control module, and carry out and control and diagnostics routines, in order to control the operation of actuator.Can carry out at certain intervals executive routine, for example during the motor just carrying out and vehicle operating every 3.125,6.25,12.5,25 and 100 milliseconds.Alternatively, can be in response to the executive routine that comes of event.
The optionally operation in one of several operating range states of exemplary power assembly, it can be described to: engine condition, it comprises one of engine operating status (ON) and engine shutdown state (OFF); And transmission state, it comprises a plurality of fixed gears and stepless change operator scheme, below with reference to table 1, is describing.
Table 1
Each in transmission operating range state is described in this table, and indication is which particular clutch C1 70, C2 62, C3 73 and C4 75 are by start for each in operating range state.The first stepless shift mode is that EVT pattern I or MI are selected by only making dynamic clutch C1 70, so that shelves connect the external gear member of third planet gear train 28.Engine condition can be one of ON (MI_Eng_On) or OFF (MI_Eng_Off).The second stepless shift mode is that EVT pattern II or MII are selected by only making dynamic clutch C2 62, axle 60 is connected to the carrier of third planet gear train 28.Engine condition can be one of ON (MII_Eng_On) or OFF (MII_Eng_Off).For the object of this description, when engine condition is OFF, motor input speed equals 0 and turns per minute (RPM), and engine crankshaft does not rotate.Fixed gear operation provides the fixed ratio operation of the input of speed changer 10 to output speed, i.e. N i/ N o, be achieved.By making dynamic clutch C1 70 and C4 75, select the first fixed gear operation (FG1).By making dynamic clutch C1 70 and C2 62, select the second fixed gear operation (FG2).By making dynamic clutch C2 62 and C4 75, select the 3rd fixed gear operation (FG3).By making dynamic clutch C2 62 and C3 73, select the 4th fixed gear operation (FG4).Input increases with fixed gear operation the fixed ratio operation of output speed, and reason is that the gear ratio in planetary pinion 24,26 and 28 reduces.Be respectively N aand N bthe first and second motors 56 and 72 the rotational speed internal rotating that depends on the mechanism as limited by clutch, and the input speed measuring with input shaft 12 places is proportional.
In response to inputting as the operator via accelerator pedal 113 and brake petal 112 who is captured by user interface 13, the output torque T of the one or more definite quilt order in HCP 5 and other control module cMD, it is intended to meet operator's torque request T o_REQ, to be performed and to transfer to power train 90 at output link 64 places.Final traffic tool acceleration is subject to the impact of other factors, for example road load, road grade and traffic tool quality.Multiple different operating characteristic based on power assembly, for speed changer 10 is determined operating range state.This comprises operator's torque request, and it is communicated to user interface 13 by accelerator pedal 113 and brake petal 112, as previously described.Operating range state can be based on power assembly torque demand, and it is by causing in order to operate the instruction of the first and second motors 56 and 72 in electric energy generate pattern or in moment of torsion generate pattern.Operating range state can be determined by optimizer, and described optimizer is the energy efficiency to the demand of power, battery charging state and motor 14 and the first and second motors 56 and 72 based on operator, determines best system effectiveness.The result of the optimizer of control system based on being performed is managed the moment of torsion input from motor 14 and the first and second motors 56 and 72, and makes thus system effectiveness optimization, manages fuel economy and battery charging.In addition, can the fault based in parts or system determine operation.HCP 5 monitoring moment of torsion generating apparatus, and determine in order to realize required output torque and meet the required output of the power from speed changer 10 of operator's torque request.As should be from the above description clearly, ESD 74 and the first and second motors 56 and 72 by electric operation connect, with kinetic current therebetween.In addition, motor 14, the first and second motors 56 and 72 and electric mechanical speed changer 10 by mechanically actuated connect, transmit betwixt power and generate the kinetic current of going to output link 64.
Fig. 3 has drawn for controlling the schematic diagram of mobile hydraulic control circuit 42 of the hydraulic oil of exemplary speed changer.Main Hydraulic Pump 88 is expelled input shaft 12 from motor 14, and service pump 110 is controlled and to hydraulic control circuit 42, provided pressure fluid by valve 140 by TPIM 19.Service pump 110 preferably includes motor-drive pump, and it has suitable size and capacity, when operation, the pressurized hydraulic oil of enough flows is provided in hydraulic control circuit 42.Hydraulic control circuit 42 optionally distributes hydraulic pressure to a plurality of devices, comprising: torque transfer clutch C1 70, C2 62, C3 73 and C4 75; Active cooling loop for the first and second motors 56 and 72; With for carry out the basic cooling circuit of Cooling and Lubricator speed changer 10 via passage 142,144.As previously stated, TCM 17 starts each clutch, by the selectivity to oil hydraulic circuit flow control device, activate and realize one of transmission operating range state, described oil hydraulic circuit flow control device comprises variable pressure control solenoid valve (PCS) PCS1 108, PCS2 112, PCS3 114, PCS4 116 and electromagnetic valve traffic management valve, X valve 119 and Y-valve 121.Hydraulic control circuit 42 is fluidly connected to pressure switch PS1, PS2, PS3 and PS4 via passage 124,122,126 and 128 respectively.Electromagnetic pressure control valve PCS1 108 has conventionally high control position, and operates in order to by adjusting the amplitude of the hydrodynamic pressure in oil hydraulic circuit with the fluid interaction effect of controllable pressure regulator 107 and guiding valve 109.Controllable pressure regulator 107 and guiding valve 109 and PCS1 108 interaction effects are controlled the hydraulic pressure in hydraulic control circuit 42, and can be provided additional function for hydraulic control circuit 42 in the pressure of certain limit.Electromagnetic pressure control valve PCS2 112 has conventionally high control position, and is fluidly connected to guiding valve 113 and goes forward side by side line operate in order to realize when activateding through flowing wherein.Guiding valve 113 is fluidly connected to pressure switch PS3 via passage 126.Electromagnetic pressure control valve PCS3 114 has conventionally high control position, and is fluidly connected to guiding valve 115 and goes forward side by side line operate in order to realize when activateding through flowing wherein.Guiding valve 115 is fluidly connected to pressure switch PS1 via passage 124.Electromagnetic pressure control valve PCS4 116 has conventionally low control position, and is fluidly connected to guiding valve 117 and goes forward side by side line operate in order to realize when activateding through flowing wherein.Guiding valve 117 is fluidly connected to pressure switch PS4 via passage 128.
X valve 119 and Y-valve 121 comprise separately the traffic management valve of being controlled by solenoid valve 118,120 respectively in example system, and have the state of a control of height (1) and low speed (0).State of a control refers to the position of controlling each valve that flows to the different device in hydraulic control circuit 42 and speed changer 10.X valve 119 operate in order to according to fluid input source respectively via fluid passage 136,138,144,142 by direct pressurized fluid to clutch C3 73 and C4 75 with for the cooling system of the stator of the first and second motors 56 and 72, as described below.Y-valve 121 operate in order to according to fluid input source respectively via fluid passage 132 and 134 by direct pressurized fluid to clutch C1 70 and C2 62, as described below.Y-valve 121 is fluidly connected to pressure switch PS2 via passage 122.
Hydraulic control circuit 42 comprises basic cooling circuit, and it is for providing the stator of cooling the first and second motors 56 of hydraulic oil and 72.Basis cooling circuit comprises fluid line, and it directly flows to from valve 140: lead to the Flow restrictor of fluid passage 144, the basic cooling circuit for the stator of the first motor 56 is led in described fluid passage 144; The Flow restrictor that leads to fluid passage 142, the basic cooling circuit for the stator of the second motor 72 is led in described fluid passage 142.Active cooling to the stator for the first and second motors 56 and 72 is realized in the following manner: selectivity actuation pressure is controlled solenoid valve PCS2 112, PCS3 114 and PCS4 116 and electromagnetic valve traffic management valve X valve 119 and Y-valve 121, it causes hydraulic oil moving around selected subflow, and allow that heat is transmitted betwixt, be mainly by conduction.
With reference to following table 2, provide a kind of example logic table of controlling the operation of speed changer 10 in of transmission operating range state in order to the control of realization example hydraulic control circuit 42.
Table 2
Low scope is defined as comprising the transmission operating range state of one of the first stepless shift mode and the operation of the first and second fixed gears.High scope is defined as comprising the transmission operating range state of one of the second stepless shift mode and the operation of the third and fourth fixed gear.The actuating of the Selective Control of X valve 119 and Y-valve 121 and solenoid valve PCS2 112, PCS3 114, PCS4 116 promotes that the mobile of hydraulic oil starts clutch C1 70, C2 63, C3 73 and C4 75, and cooling to stator and the first and second motors 56 and 72 is provided.
In operation, transmission operating range state, i.e. one of fixed gear and stepless shift mode operation, the multiple different operating characteristic based on power assembly is selected to for exemplary speed changer 10.This comprises operator's torque request, conventionally by input, is communicated to UI 13, as previously described.Operating range state can be determined by optimizer, and described optimizer can operate with the energy efficiency based on operator's torque request, battery charging state and motor 14 and the first and second motors 56 and 72, determines best system effectiveness.The result of the optimizer of control system based on being performed is managed the input torque from motor 14 and the first and second motors 56 and 72, and carries out system optimization, improves fuel economy and manages battery charging.
As mentioned above, the object of hydraulic control system is to provide pressurized hydraulic oil and runs through hybrid power assembly and realize a plurality of functions.It will be understood by those of skill in the art that: to the control of hydraulic control system to allow by the steady with consistent action need understanding P of the function that the supply of flow of pressurized realizes is provided lINE.P lINEthe ability that meets the necessary hydraulic control system of required function for understanding is important.P lINEfor the operation of a pump of management or a plurality of pumps, be also important, a described pump or a plurality of pump are utilized to provide to hydraulic control system the supply of flow of pressurized.
P lINEthe ability that hydraulic control system possesses to meet required function is described.For example, in Clutch Control function, P lINEclutch obtainable maximum fastening force is immediately described.As described above, clutch depends in order to transmit the ability of reaction torque the fastening force that is applied to clutch.In addition will be appreciated that: P lINEhow soon describe clutch can be filled.In another example, it will be understood by those of skill in the art that: cooling with respect to motor, by motor, bring into play base machine refrigerating function or the machine refrigerating function of optionally taking the initiative, pass the hydraulic pressure oil mass of heat exchange mechanism of motor and the gained heat exchanging function of the gained heat exchange mechanism of motor and function as P lINEfunction and rise.In another example, hydraulic oil can be used for lubricating fitting, for example bearing.Through fixed orifice, to the gained of device, flow and flow of pressurized is P in order to meet the gained ability of lubricating function lINEfunction.
The clutch device hydraulically being started adopts the pressurized stream optionally starting of hydraulic fluid, generates required clutch moment of torque ability when clutch is activated and be engaged.Embodiment relates to required clutch moment of torque ability, and it is corresponding to the required minimum clutch moment of torque ability of sliding phenomenon of eliminating in the clutch device that has been activated and has engaged.Fig. 4 shows according to a kind of controller of the present disclosure, and it is for predicting one or more clutch load that has started clutch device, and adjusting is applied to one or more hydraulic line pressure that started clutch device.Controller 400 can be embodied in the control module 5 of Fig. 2.Controller 400 comprises ECM 23, UI 13, predictability power assembly parameter module 402, transient state power assembly parameter module 404, power loss optimizer 405, cost hysteresis block 414, estimating clutch load module 416, reaction clutch load management module 418 and line pressure (P lINE) control module 420.
Power loss optimizer 405 is that a plurality of each that obtain in Engine torque are repeatedly determined running cost based on operator's torque request, and will have the Engine torque (T of minimum power assembly running cost e) be chosen as optimal engine moment of torsion (T e_OPT).Corresponding to T e_OPTprediction clutch load may be utilized preemptively (preemptively) to regulate to be applied to the hydraulic line pressure (P of one or more clutch device lINE).For example, one or more clutch device can comprise C1 70, C2 62, C3 73 and C4 75, and it is activated and engages in event on the horizon based on operator's torque request is predicted.Power loss optimizer 405 comprises optimizes module 406, cost function module (cost function module) 408, search function module (search function module) 410 and determination module 412.
ECM 23 by from minimum, permitted to hold Engine torque to maximum, permitted to hold Engine torque certain limit permitted hold Engine torque 451 and be input to search function module 410.Should be understood that: permitted to hold Engine torque 451 corresponding to given engine condition, wherein power loss optimizer 405 can repeatedly be determined running cost for a plurality of each that obtain Engine torque for one or more engine conditions.UI 13 is input to operator's torque request 450 in search function module 410 and predictability power assembly parameter module 402.Search function module 410 is carried out search during each repetition of power loss optimizer 405, come to determine to be provided to determination module 412, to optimize each the Engine torque T in module 406 and cost function module 408 e460.In an exemplary embodiment, search function module 410 is carried out gold search method, to use gold ratio (golden ratio) to determine T during each repetition e460.Alternatively, search function module 410 can be used any suitable search method, for repeat to determine T at every turn e460.During repeating for the first time, by the definite T of search function module 410 e460 are selected as optimal engine moment of torsion.Yet, by power loss optimizer 405, carry out the T that minimum power assembly running cost is afterwards associated with all repetition e460 will be selected as optimal engine torque T e_OPT.
Predictability power assembly parameter module 402 receives operator's torque request 450, and predicts first group of a plurality of power assembly parameter 452, and it is input to optimizes module 406.First group of a plurality of power assembly parameter 452 of prediction can comprise: for the prediction clutch state of one or more clutches; Prediction output torque; Prediction engine speed; The prediction motor torque limit; The prediction clutch moment of torque limit; With the prediction electrical energy storage device power limit.For a plurality of, permitted to hold each in Engine torque 451, optimize module 406 and determine output 456, its indication predicting output torque and prediction clutch load, its first group of a plurality of power assembly parameters 452 based on prediction minimize total output assembly running cost.
In at every turn the repeating of power loss optimizer 405, cost function module 408 receives: the prediction output torque that carrys out the output 456 of self-optimizing module 406; Engine torque T from search function module 410 e460; With second group of a plurality of power assembly parameter 454 from transient state power assembly parameter module 404.Transient state power assembly parameter module 404 is based on second group of a plurality of power assembly parameter 454 of operator's torque request 450 outputs.Second group of a plurality of power assembly parameter 454 comprises output speed and operator's torque request of electrical energy storage device charged state, the traffic tool.Therefore, cost function module 408 is determined the power assembly running cost 458 during each repetition, wherein repeats corresponding to a plurality of corresponding of obtaining in Engine torque at every turn.Then power assembly running cost 458 is input to search function module 410, carries out search here and comes for follow-up repetition.
Therefore, cost function module 408 each obtainable Engine torque of monitoring and each corresponding prediction output torque, it minimizes total output assembly running cost, monitors second group of a plurality of power assembly parameter 454 simultaneously.Then, for each obtainable Engine torque and each corresponding prediction output torque, cost function module 408 is determined power assembly running cost 458 based on second group of a plurality of power assembly parameter.Once after having repeated all, determination module 412 is selected a plurality of Engine torque (T with minimum power assembly running cost that obtain in Engine torque e460), for example determination module 412 is selected T e_OPT.Determination module 412 further receives output 456, and its indication is for each prediction clutch load repeating.Therefore, determination module 412 is further determined prediction clutch load, and it is determined to for T e_OPT, as optimum prediction clutch load 462.
At power loss optimizer 405, repeatedly determine in the embodiment of running cost optimal engine torque T for each a plurality of each that obtain in Engine torque for a plurality of engine conditions e_OPTby determination module 412, selected for each engine condition.The T with minimum power assembly running cost in a plurality of engine conditions e_OPTbe selected as final Engine torque T e_Final.Therefore, determination module 412 is further determined prediction clutch load, and it is determined to for T e_Final, as final prediction clutch load.In addition, cost hysteresis block 414 can be utilized to apply stablizes the cost minimum power assembly running cost in engine condition at the most, for example, with T e_Finalthe power assembly running cost being associated.The amplitude that stable cost has is enough to avoid, from the engine condition corresponding to final Engine torque, any vibration occurs.Therefore, when stable processing is employed, the final prediction clutch load 464 of cost hysteresis block output stabilization.405 of power cost optimizers will be appreciated that: if, for to determine running cost for a plurality of each that obtain Engine torque of an engine condition, can be walked around cost hysteresis block 414.
Will be appreciated that: power assembly running cost is associated with traffic tool steerability, fuel economy, electrical energy storage device utilization ratio and discharges relevant running cost.Running cost can comprise engine power loss, motor power loss, electrical energy storage device power loss, break power loss and machine power loss, and it is associated with for motor 14 and non-burning motor 56 and 72 operations of multi-mode power assembly being carried out at particular point of operation place.Therefore, lower running cost can be associated with high conversion efficiency, carry out compared with low fuel consumption, lower electrical energy storage device power utilization rate and for each engine speed/load operation point compared with low emission, and the candidate operations state of motor 14 is included in and is considered.
Reaction clutch load management module 418 is for each optimum prediction clutch load 462 of relatively being determined by determination module 412 in one or more clutch device (or final prediction clutch load 464 of being determined by cost hysteresis block 414) and by the definite estimating clutch load 466 of estimating clutch load module 416.Estimating clutch load 466 can add P corresponding to the estimation transient state clutch load for one or more each by the clutch device of start and joint lINEpredetermined nargin.For example, when the prediction clutch load that has a minimum power assembly running cost when optimum prediction clutch load 462 (or prediction clutch load 464 of stabilization) is greater than estimating clutch load 466, reaction clutch load management module 418 is determined adjusted hydraulic line pressure P lINE_ADJ468, it is applied to the one or more clutch device that are activated and are engaged for event on the horizon.For example, for each in one or more clutch device, when optimum prediction clutch load 464 is greater than estimating clutch load 466, P lINE_ADJ468 will be applied to the P of one or more clutch device lINEincrease an amplitude, it surpasses the amount of estimating clutch load 466 corresponding to optimum prediction clutch load 464.P lINE_ADJ468 maintain minimum P lINErealize prediction clutch load (for example, the final prediction clutch load of optimum prediction clutch load or stabilization), it is determined to Engine torque (for example, the T for having minimum power assembly running cost e_OPTor T e_Final).Therefore, for maintaining minimum P lINEp lINE_ADJ468 are provided to P lINEcontrol module 420, comes according to P lINE_ADJthe interior transmission hydraulic line pressure of 468 hydraulic control circuit 42 at Fig. 3.
Will be appreciated that: when optimum prediction clutch load 462 (or prediction clutch load 464 of stabilization) is not more than estimating clutch load 466, be applied to the P of one or more clutch device lINEcorresponding to estimating clutch load, estimate that transient state clutch load adds P lINEpredetermined nargin.
Fig. 5 shows according to the flow chart that regulates the hydraulic line pressure that is applied to one or more clutch device with the controller 400 of Fig. 4 of the present disclosure.For the sake of simplicity, this flow chart only regulates by discussing the hydraulic line pressure that is applied to a clutch device, yet this flow chart is equally applicable to regulate the hydraulic line pressure that is applied to more than one clutch device.Table 3 is provided as the key of this flow chart, and wherein the frame of figure notation and corresponding function are given as follows.
Table 3
Flow chart starts from frame 501, and predicts first group of a plurality of power assembly parameter 452 at frame 502 places.Based on operator's torque request 450 in first group of a plurality of power assembly parameter 452 of the interior prediction of predictability power assembly parameter module 402.As previously mentioned, first of prediction group of a plurality of power assembly parameter 452 can comprise: prediction clutch state; Prediction output torque; Prediction engine speed; The prediction motor torque limit; The prediction clutch moment of torque limit; With the prediction electrical energy storage device power limit.
At frame 504 places, for each obtainable T e, by optimizing the definite minimized prediction clutch of total output assembly running cost load and the prediction output torque of making of module 406.As previously mentioned, ECM 23 by from minimum, permitted to hold Engine torque to maximum, permitted to hold Engine torque certain limit permitted hold Engine torque 451 and be input to search function module 410.
At power loss optimizer 405, repeatedly determine in the embodiment of running cost for each a plurality of each that obtain in Engine torque for a plurality of engine conditions, the frame 504 that uses optimization module 406 is further each definite prediction output torque and the prediction clutch load in a plurality of engine conditions, and wherein each engine condition comprises a plurality of Engine torques that obtain accordingly.
At frame 506 places, by determination module 412, selected to have the T of minimum power assembly running cost e.The selected T as previously mentioned, with minimum power assembly running cost ecan be called as optimal engine torque T e_OPT.Based on second group of a plurality of power assembly parameter 454, by cost function module 408, be identified for each T e460 power assembly running cost, and indication is corresponding to T ethe output 456 of 460 prediction output torque inputs to cost function module 408.As previously mentioned, second group of a plurality of power assembly parameter 454 comprises electrical energy storage device charged state, output speed and operator's torque request 450.
At power loss optimizer 405, for each a plurality of each that obtain in Engine torque for a plurality of engine conditions, repeatedly determine in the embodiment of running cost, use the frame 506 of determination module 412 further for each selection in a plurality of engine conditions, to there is the T of minimum power assembly running cost e, wherein each engine condition comprises corresponding a plurality of Engine torques that obtain.Therefore, each engine condition comprises corresponding optimal engine torque T e_OPT.For example, can be the Engine torque that the first, second, third and the 4th engine condition selects to have minimum power assembly running cost.In an exemplary embodiment, the first engine condition can comprise that all cylinders are all supplied to fuel; The second engine condition can comprise that all cylinders are not supplied to fuel; Trimotor state can comprise that half cylinder is supplied to fuel; And the 4th engine condition can comprise that half cylinder is not supplied to fuel.Then, determination module 412 selects to have the final Engine torque T of minimum power assembly running cost in a plurality of engine conditions e_Final.The T in other words, in a plurality of engine conditions with minimum power assembly running cost e_OPTby determination module 412, be chosen as T e_Final.
At frame 508 places, the T based on thering is minimum power assembly running cost eregulate the hydraulic line pressure P that is applied to clutch lINE.For example, when prediction clutch load (, the final clutch load 464 of best clutch load 462 or stabilization) is greater than estimating clutch load 466, by reaction clutch load management module 418, determine adjusted hydraulic line pressure P lINE_ADJ468.P lINE_ADJ468 are determined to maintain the T that has minimum power assembly running cost for being embodied as ethe minimum P of definite prediction clutch load 464 lINE.The T as previously mentioned, with minimum power assembly running cost ecorresponding to T e_OPT, or when more than one engine condition is optimized, there is the T of minimum power assembly running cost ecorresponding to T e_Final.Then, P lINEcontrol module 420 is according to P lINE_ADJthe interior transmission hydraulic line pressure of 468 hydraulic control circuit 42 at Fig. 3.
The disclosure has been described some preferred embodiment and modification thereof.Those skilled in the art can expect other modification and change when reading and understanding specification.Therefore, anticipate and seek for the disclosure and be not limited to as the disclosed specific embodiment for implementing the contemplated optimal mode of the disclosure, but the disclosure should comprise all embodiments that fall within the scope of appended claims.

Claims (10)

1. for regulating the method for hydraulic line pressure, described hydraulic line pressure is applied to the clutch device in electric mechanical speed changer, described electric mechanical speed changer by mechanically actuated be attached to explosive motor and at least one motor, described method comprises:
Based on operator's torque request, be first group of a plurality of power assembly parameter of event prediction on the horizon;
Based on first group that predicts a plurality of power assembly parameters, for a plurality of each that obtain in Engine torque, determine and make the minimized prediction clutch of total output assembly running cost load and prediction output torque; And
From described, a plurality ofly obtain the Engine torque based on thering is minimum power assembly running cost Engine torque and regulate hydraulic line pressure.
2. the method for claim 1, wherein when when thering is the definite prediction clutch load of Engine torque of minimum power assembly running cost and be greater than estimating clutch load, regulate hydraulic line pressure.
3. method as claimed in claim 2, wherein, is adjusted to hydraulic line pressure to maintain the minimum hydraulic pressure line pressure that has the definite prediction clutch load of the Engine torque of minimum power assembly running cost for being embodied as.
4. the method for claim 1, wherein by gold ratio function of search, determine the Engine torque with minimum power assembly running cost.
5. method as claimed in claim 4, wherein, gold ratio function of search carrys out to determine the Engine torque with minimum power assembly running cost in the following manner:
Monitor each obtainable Engine torque and make minimized each the corresponding prediction output torque of total output assembly running cost;
Monitor second group of a plurality of power assembly parameter;
Based on described second group of a plurality of power assembly parameter, for each obtainable Engine torque and each, predict accordingly output torque and determine power assembly running cost; And
Based on determined power assembly running cost, from a plurality of obtainable Engine torques, select to have the Engine torque of minimum power assembly running cost.
6. the method for claim 1, wherein for first group of a plurality of power assembly parameter of the prediction of event on the horizon, comprise: for the prediction clutch state of described clutch device; Prediction output torque; Prediction engine speed; The prediction motor torque limit; The prediction clutch moment of torque limit; With the prediction electrical energy storage device power limit.
7. method as claimed in claim 5, wherein, described second group of a plurality of power assembly parameter comprise: electrical energy storage device charged state; Output speed; With operator's torque request.
8. the method for claim 1, wherein described event on the horizon comprises shift of transmission, the combination in any that output torque changes and Engine torque changes.
9. for regulating the method for hydraulic line pressure, described hydraulic line pressure is applied to the one or more clutch device in electric mechanical speed changer, described electric mechanical speed changer by mechanically actuated be attached to explosive motor and at least one motor, described method comprises:
Based on operator's torque request, be first group of a plurality of power assembly parameter of event prediction on the horizon, described event on the horizon comprises shift of transmission, the combination in any that output torque changes and Engine torque changes;
For have separately in corresponding a plurality of a plurality of engine conditions that obtain Engine torque each,
Based on first group that predicts a plurality of power assembly parameters be described a plurality of each acquisition in Engine torque be identified in one or more clutch device each prediction clutch load and make the minimized prediction output torque of total output assembly running cost, and
From described a plurality of Engine torques of selecting to have minimum power assembly running cost Engine torque that obtain; And
Final Engine torque based on having minimum power assembly running cost from a plurality of engine conditions regulates hydraulic line pressure.
10. for controlling an equipment for power assembly, comprising:
Electric mechanical speed changer, its by mechanically actuated be attached to explosive motor and at least one motor, described explosive motor and at least one motor are suitable for being come to output link transmit machine power optionally by the clutch device of hydraulically start via selectivity start is one or more; With
Controller, it is embodied in control module, comprises
Predictability power assembly parameter module, it is configured in order to predict first group of a plurality of power assembly parameter in event on the horizon;
Optimize module, it is configured in order to based on operator's torque request and the first group of a plurality of power assembly parameter predicting, and is a plurality of each the definite minimized prediction clutch of total output assembly running cost load and prediction output torques of making that obtain in Engine torque; With
Line pressure control module, it is configured in order to regulate based on described a plurality of Engine torques in Engine torque with minimum power assembly running cost that obtain the hydraulic line pressure that is applied to clutch device.
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DE102014101736A1 (en) 2014-08-21
CN104006152B (en) 2016-09-07

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